JP4952414B2 - Tube for heat exchanger - Google Patents

Tube for heat exchanger Download PDF

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Publication number
JP4952414B2
JP4952414B2 JP2007181965A JP2007181965A JP4952414B2 JP 4952414 B2 JP4952414 B2 JP 4952414B2 JP 2007181965 A JP2007181965 A JP 2007181965A JP 2007181965 A JP2007181965 A JP 2007181965A JP 4952414 B2 JP4952414 B2 JP 4952414B2
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inner fin
plate
curved
tubular member
peripheral surface
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JP2009019799A (en
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貴英 大原
典幸 宮崎
充克 斉藤
宇 王
典生 吉田
哲哉 榊原
一浩 光川
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Denso Corp
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Denso Corp
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Priority to JP2007181965A priority Critical patent/JP4952414B2/en
Priority to PCT/JP2008/001850 priority patent/WO2009008172A1/en
Priority to US12/515,392 priority patent/US8925625B2/en
Priority to BRPI0806229A priority patent/BRPI0806229B8/en
Priority to CN200880003191XA priority patent/CN101595360B/en
Priority to DE112008001782T priority patent/DE112008001782T5/en
Publication of JP2009019799A publication Critical patent/JP2009019799A/en
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Description

本発明は、熱交換器用チューブに関するものであり、例えば、自動車のラジエータ等への適用に有用である。   The present invention relates to a heat exchanger tube, and is useful for application to, for example, a radiator of an automobile.

従来、チューブ内部にインナーフィンを設けた熱交換器用チューブが知られている（例えば、特許文献１参照）。この特許文献１に記載の熱交換器用チューブにおけるチューブは、断面が扁平形状に形成されており、チューブ短径方向において平行に対向する一対の平面部と長径方向において対向する弧状の湾曲部から構成されている。この扁平形状のチューブの長径方向における一方の湾曲部のみに、チューブの長手方向（熱交換媒体流れ方向）に連続する接合部を有しており、この接合部を形成する前にインナーフィンをチューブ内に配設している。 Conventionally, a heat exchanger tube in which an inner fin is provided inside the tube is known (see, for example, Patent Document 1). Tube in the heat exchanger tube described in Patent Document 1, in cross-section is formed in a flat shape, the curved portion of the arcuate opposed to each other in the pair of plane portions and the major axis direction opposed to the flat line in the tube minor axis It is configured. Only one curved portion in the major axis direction of this flat tube has a joint portion that is continuous in the longitudinal direction of the tube (heat exchange medium flow direction), and the inner fin is tubed before forming this joint portion. It is arranged inside.

ところで、特許文献１に記載の熱交換器用チューブのインナーフィンは、チューブにおける一対の平面部に挟持された状態で接合されているが、インナーフィンの両端部においてはチューブの平面部および湾曲部のいずれにも接合されていない。そのため、インナーフィンを配設する際の配設位置のずれ、接合面積が小さいことによるろう付け不良などが発生する可能性がある。   By the way, although the inner fin of the tube for heat exchangers described in Patent Document 1 is joined in a state of being sandwiched between a pair of flat portions of the tube, the flat portion of the tube and the curved portion of the inner fin are joined to each other. It is not joined to either. For this reason, there is a possibility that a disposition position when the inner fin is disposed, a brazing defect due to a small joining area, and the like occur.

また、チューブは、一枚の板状部材を接合して構成しているため、板状部材の接合面等の隙間が比較的大きな箇所では、ろう付け接合時のろう材回りが不十分となり接合不良が発生しやすいという問題がある。これにより、熱交換器からの液体漏れを引き起こす可能性がある。   In addition, since the tube is constructed by joining a single plate-like member, the brazing material around the brazing joint becomes insufficient when the gap such as the joining surface of the plate-like member is relatively large. There is a problem that defects are likely to occur. This can cause liquid leakage from the heat exchanger.

本発明は、上記点に鑑み、上述の熱交換器用チューブのチューブ内部に設けられたインナーフィンの配設性を確保しつつ、熱交換器用チューブの接合部におけるろう付け性を向上させることを目的とする。   SUMMARY OF THE INVENTION In view of the above points, the present invention aims to improve the brazing property at the joint portion of the heat exchanger tube while ensuring the disposition of the inner fin provided inside the tube of the heat exchanger tube. And

上記目的を達成するため、請求項１に記載の発明では、熱交換媒体が流通するとともに、熱交換媒体の流通方向と直交する流路断面が扁平形状に形成された板状部材からなる筒状部材（２０）と、筒状部材（２０）の内部に設けられ、熱交換媒体との伝熱面積を増大させるインナーフィン（２５）とがろう付けにより接合された熱交換器用チューブにおいて、筒状部材（２０）は、筒状部材（２０）の流路断面の短径方向において並行に対向する一対の平板部（２１、２２）と、筒状部材（２０）の流路断面の長径方向において筒状部材（２０）の両端部の内面側が弧状に形成された一対の弧状湾曲部（２３、２４）とを有しており、インナーフィン（２５）は、弧状湾曲部（２３、２４）の内面に対向する端部が、弧状湾曲部（２３、２４）の内周面に沿って密接するように形成されており、
筒状部材（２０）は、一対の弧状湾曲部（２３、２４）のうち少なくとも一方の弧状湾曲部（２３、２４）に板状部材相互の接合部を有し、この接合部において板状部材の一端部であって弧状に形成された第１湾曲部（２６）と、第１湾曲部（２６）の内周面に重ね合うように弧状に形成された第２湾曲部（２７）とが接合されており、
第２湾曲部（２７）における少なくとも第１湾曲部（２６）の先端部位（２６ａ）の内周面に対向する部位の外周面に、この外周面の周方向に延びる平坦部（２７ａ）が形成され、
前記平坦部（２７ａ）は湾曲面の一部を平坦にした段差のない形状で前記第２湾曲部（２７）の外周面に接続され、
第１湾曲部（２６）の先端部位（２６ａ）が平坦部（２７ａ）上に重ね合うようになっていることを特徴とする。 In order to achieve the above object, in the first aspect of the present invention, the heat exchange medium circulates, and the tubular shape is made of a plate-like member in which the flow channel cross section perpendicular to the flow direction of the heat exchange medium is formed in a flat shape. In the heat exchanger tube, the member (20) and the inner fin (25) which is provided inside the tubular member (20) and increases the heat transfer area with the heat exchange medium are joined by brazing. The member (20) includes a pair of flat plate portions (21, 22) facing in parallel in the minor axis direction of the channel cross section of the cylindrical member (20), and the major axis direction of the channel cross section of the cylindrical member (20). The cylindrical member (20) has a pair of arc-shaped curved portions (23, 24) in which the inner surface sides of both end portions are formed in an arc shape, and the inner fin (25) has an arc-shaped curved portion (23, 24). The end facing the inner surface is an arcuate curved portion (23, 24 Is formed so as to closely along the inner peripheral surface of,
The tubular member (20) has a joint between the plate-like members at at least one of the arc-shaped curved portions (23, 24) of the pair of arc-shaped curved portions (23, 24). The first curved portion (26) formed in an arc shape at one end of the first curved portion and the second curved portion (27) formed in an arc shape so as to overlap the inner peripheral surface of the first curved portion (26) are joined together. Has been
A flat portion (27a) extending in the circumferential direction of the outer peripheral surface is formed on the outer peripheral surface of the second curved portion (27) facing at least the inner peripheral surface of the distal end portion (26a) of the first curved portion (26). And
The flat portion (27a) is connected to the outer peripheral surface of the second curved portion (27) in a shape having no step where a part of the curved surface is flattened,
The tip portion (26a) of the first bending portion (26) is overlapped on the flat portion (27a) .

これにより、筒状部材（２０）内に設けられたインナーフィン（２５）は、その端部と対向する筒状部材（２０）端部を形成する弧状湾曲部（２３、２４）とが互いの反力で突っ張る構造とすることができる。その結果、インナーフィン（２５）の配置ずれを抑制でき、インナーフィン（２５）と筒状部材（２０）内面とを確実にろう付けすることができる。さらに、筒状部材（２０）の弧状湾曲部（２３、２４）とインナーフィン（２５）の両端部に反力を発生させることで、筒状部材（２０）における平板部（２１、２２）とインナーフィン（２５）の接触する面とを確実にろう付けすることができる。
これに加え、請求項１に記載の発明では、内周側の第２湾曲部（２７）における、少なくとも外周側の第１湾曲部（２６）の先端部位（２６ａ）の内周面に対向する部位の外周面に、この外周面の周方向に延びる平坦部（２７ａ）を形成し、この平坦部（２７ａ）は湾曲面の一部を平坦にした段差のない形状で第２湾曲部（２７）の外周面に接続し、外周側の第１湾曲部（２６）の先端部位（２６ａ）が、上記周方向に延びる平坦部（２７ａ）上に重ね合うようになっている。
この構成によれば、板状部材の長さ方向寸法にバラツキがあっても、外周側の第１湾曲部（２６）の先端部位（２６ａ）が、内周側の第２湾曲部（２７）の外周面に形成された周方向に延びる平坦部（２７ａ）上で移動することにより、板状部材の長さ方向寸法のバラツキを吸収できる。
ここで、請求項１に記載の発明における弧状とは、円弧状、楕円形状や曲率半径の異なる円弧を組合せて形成される形状を含むものである。 As a result, the inner fin (25) provided in the cylindrical member (20) has an arcuate curved portion (23, 24) that forms the end of the cylindrical member (20) facing the end thereof. The structure can be stretched by reaction force. As a result, the displacement of the inner fin (25) can be suppressed, and the inner fin (25) and the inner surface of the tubular member (20) can be brazed reliably. Further, by generating reaction forces on the arcuate curved portions (23, 24) of the tubular member (20) and both ends of the inner fin (25), the flat plate portions (21, 22) of the tubular member (20) The surface to which the inner fin (25) contacts can be brazed reliably.
In addition to this, in the first aspect of the present invention, at least the inner peripheral surface of the distal end portion (26a) of the first curved portion (26) on the outer peripheral side in the second curved portion (27) on the inner peripheral side is opposed. A flat portion (27a) extending in the circumferential direction of the outer peripheral surface is formed on the outer peripheral surface of the portion, and the flat portion (27a) is a second curved portion (27 having a flat shape with no step and having a flat portion. ) And the distal end portion (26a) of the first curved portion (26) on the outer peripheral side overlaps the flat portion (27a) extending in the circumferential direction.
According to this configuration, even if the lengthwise dimension of the plate-like member varies, the distal end portion (26a) of the first curved portion (26) on the outer peripheral side is the second curved portion (27) on the inner peripheral side. By moving on the flat portion (27a) extending in the circumferential direction formed on the outer peripheral surface of the plate member, it is possible to absorb variations in the lengthwise dimension of the plate-like member.
Here, the arc shape in the invention described in claim 1 includes an arc shape, an elliptical shape, and a shape formed by combining arcs having different curvature radii.

また、請求項２に記載の発明のように、請求項１に記載の熱交換器用チューブにおいて、筒状部材（２０）とインナーフィン（２５）は、１枚の板状部材により一体に形成してもよい。請求項２に記載の発明によれば、１枚の板状部材により筒状部材（２０）とインナーフィン（２５）を一体に形成する場合に、インナーフィン（２５）と筒状部材（２０）との接合部のろう付け性を向上させることができる。 It is preferable as defined in claim 2, in the heat exchanger tube of claim 1, the inner fin tubular member (20) (25) is formed integrally by a plate-like member May be. According to the second aspect of the present invention, when the tubular member (20) and the inner fin (25) are integrally formed by a single plate-like member , the inner fin (25) and the tubular member (20). It is possible to improve the brazing property of the joint portion.

また、請求項３に記載の発明のように、請求項２に記載の熱交換器用チューブにおいて、弧状湾曲部（２３、２４）と、インナーフィン（２５）における前記弧状湾曲部（２３、２４）の内周面とが密接している部位の接触角度は、１１０°以上とすることで、筒状部材（２０）とインナーフィン（２５）との間のろう付け性を安定させることができる。ここで接触角度θとは、弧状湾曲部（２３、２４）の弧中心点から弧状湾曲部（２３、２４）とインナーフィン（２５）の端部とが密接する部位の両端部に延びる方向がなす角度を示している。 Further, as in the invention according to claim 3, in the heat exchanger tube according to claim 2, the arc-shaped curved portion (23, 24) and the arc-shaped curved portion (23, 24) in the inner fin (25). By setting the contact angle of the portion in close contact with the inner peripheral surface to 110 ° or more, the brazing property between the tubular member (20) and the inner fin (25) can be stabilized. Here, the contact angle θ is a direction extending from the arc center point of the arc-shaped curved portion (23, 24) to both ends of the portion where the arc-shaped curved portion (23, 24) and the end of the inner fin (25) are in close contact with each other. The angle to make is shown.

また、請求項４に記載の発明のように、請求項１に記載の熱交換器用チューブにおいて、筒状部材（２０）とインナーフィン（２５）は、それぞれ異なる板状部材で構成してもよい。請求項４に記載の発明によれば、筒状部材（２０）の板厚とインナーフィン（２５）の板厚とを変更することができる。ここで筒状部材（２０）は、熱交換器用チューブの外殻をなすものであり耐圧性、強度等の理由から所定の板厚の板状部材を用いることができる。一方、インナーフィン（２５）は、熱交換性、軽量化のため筒状部材（２０）よりも板厚の薄い板状部材を用いることができる。 Moreover, like the invention of Claim 4, in the tube for heat exchangers of Claim 1, you may comprise a cylindrical member (20) and an inner fin (25) with a respectively different plate-shaped member. . According to invention of Claim 4, the board thickness of a cylindrical member (20) and the board thickness of an inner fin (25) can be changed. Here, the cylindrical member (20) forms the outer shell of the heat exchanger tube, and a plate-like member having a predetermined thickness can be used for reasons such as pressure resistance and strength. On the other hand, for the inner fin (25), a plate-like member having a plate thickness thinner than that of the cylindrical member (20) can be used for heat exchange and weight reduction.

また、請求項５に記載の発明のように、請求項１ないし４のいずれか１つに記載の熱交換器用チューブにおいて、第１湾曲部（２６）の先端部位（２６ａ）は、先端に向かって前記板状部材の板厚さ方向の断面積が徐々に減少するように形成されている。これによると、第１湾曲部２６と第２湾曲部２７とを接合する際、筒状部材（２０）の外周面にできる段差（隙間）の形成を抑制することができる。 Further, as in the invention described in claim 5, in the heat exchanger tube according to any one of claims 1 to 4, the tip portion (26a) of the first bending portion (26) faces the tip. The cross-sectional area of the plate member in the plate thickness direction is gradually reduced. According to this, when joining the 1st bending part 26 and the 2nd bending part 27, formation of the level | step difference (gap) which can be made on the outer peripheral surface of a cylindrical member (20) can be suppressed.

なお、上記各手段の括弧内の符号は、後述する実施形態に記載の具体的手段との対応関係を示すものである。   In addition, the code | symbol in the bracket | parenthesis of each said means shows the correspondence with the specific means as described in embodiment mentioned later.

（第１実施形態）
以下、本発明の第１実施形態について図１〜図４に基づいて説明する。本第１実施形態は、本発明に係るインナーフィンチューブ２（熱交換器用チューブ）を、車両用エンジン（内燃機関）を冷却したエンジン冷却水（熱媒体）と空気（大気）とを熱交換するラジエータ１のインナーフィンチューブ２に適用したものである。 (First embodiment)
Hereinafter, a first embodiment of the present invention will be described with reference to FIGS. In the first embodiment, the inner fin tube 2 (heat exchanger tube) according to the present invention exchanges heat between engine coolant (heat medium) that cools a vehicle engine (internal combustion engine) and air (atmosphere). This is applied to the inner fin tube 2 of the radiator 1.

ここで、図１は本実施形態におけるラジエータ１を示す正面図を示している。   Here, FIG. 1 has shown the front view which shows the radiator 1 in this embodiment.

図１における、インナーフィンチューブ２は、エンジン冷却水が流れる管である。このインナーフィンチューブ２は、空気の流通方向（紙面垂直方向）が長径方向と一致するように扁平状に形成されている。また、インナーフィンチューブ２の長手方向が水平方向に一致するように鉛直方向に複数本平行に配置されている。このインナーフィンチューブ２の構造の詳細については後述する。   The inner fin tube 2 in FIG. 1 is a tube through which engine coolant flows. The inner fin tube 2 is formed in a flat shape so that the air flow direction (perpendicular to the paper surface) coincides with the major axis direction. Further, a plurality of inner fin tubes 2 are arranged in parallel in the vertical direction so that the longitudinal direction thereof coincides with the horizontal direction. Details of the structure of the inner fin tube 2 will be described later.

インナーフィンチューブ２の空気の流通方向と平行な面における両外側面には波状に成形されたアウターフィン３が接合されている。このアウターフィン３により空気との伝熱面積を増大させてエンジン冷却水と空気との熱交換を促進している。以下、インナーフィンチューブ２およびアウターフィン３からなる熱交換部をコア部４と呼ぶ。   Outer fins 3 formed in a wave shape are joined to both outer side surfaces of the inner fin tube 2 parallel to the air flow direction. The outer fin 3 increases the heat transfer area with air to promote heat exchange between the engine coolant and air. Hereinafter, the heat exchanging part composed of the inner fin tube 2 and the outer fin 3 is referred to as a core part 4.

ヘッダタンク５は、インナーフィンチューブ２の長手方向端部（本実施形態では、左右端）にてインナーフィンチューブ２の長手方向と直交する方向（本実施形態では、鉛直方向）に延びて複数のインナーフィンチューブ２と連通している。   The header tank 5 extends in a direction (vertical direction in the present embodiment) orthogonal to the longitudinal direction of the inner fin tube 2 at the longitudinal end portions (in the present embodiment, left and right ends) of the inner fin tube 2. It communicates with the inner fin tube 2.

このヘッダタンク５は、インナーフィンチューブ２が挿入接合されたコアプレート５ａと、コアプレート５ａとともにタンク内空間を構成するタンク本体５ｂとを有して構成されている。なお、本実施形態では、コアプレート５ａは金属（例えば、アルミニウム合金）製であり、タンク本体５ｂは樹脂製である。   The header tank 5 includes a core plate 5a to which the inner fin tube 2 is inserted and joined, and a tank body 5b that constitutes a space in the tank together with the core plate 5a. In the present embodiment, the core plate 5a is made of metal (for example, aluminum alloy), and the tank body 5b is made of resin.

また、コア部４の両端部には、インナーフィンチューブ２の長手方向と略平行に延びてコア部４を補強するインサート６が設けられている。   Further, inserts 6 that reinforce the core portion 4 by extending substantially parallel to the longitudinal direction of the inner fin tube 2 are provided at both ends of the core portion 4.

次に、本実施形態のインナーフィンチューブ２の構造の詳細について図２に基づいて説明する。図２（ａ）は、インナーフィンチューブ２の冷却水流通方向と直交する断面の断面図を示している。図２（ｂ）は、図２（ａ）に示すＡ部における部分拡大断面図である。 Next, the detail of the structure of the inner fin tube 2 of this embodiment is demonstrated based on FIG. 2 (a) is a cross-sectional view of a cross section perpendicular to the coolant flow direction of the inner fin tube 2. FIG. 2B is a partially enlarged cross-sectional view of a portion A shown in FIG.

図２に示すように、インナーフィンチューブ２には、インナーフィンチューブ２の外殻を構成しエンジン冷却水流れ方向に直交する断面が扁平形状に形成された筒状部材２０と、筒状部材２０内に設けられエンジン冷却水との伝熱面積を増大させるインナーフィン２５から構成されている。   As shown in FIG. 2, the inner fin tube 2 includes a tubular member 20 that forms an outer shell of the inner fin tube 2 and has a flat cross section perpendicular to the engine coolant flow direction, and the tubular member 20. It is comprised from the inner fin 25 which is provided in the inside and increases a heat transfer area with engine cooling water.

扁平形状に形成された筒状部材２０は、短径方向において平行に対向する第１平板部２１および第２平板部２２と、長径方向においてそれぞれ外側に突出し円弧状に形成された第１円弧状湾曲部２３および第２円弧状湾曲部２４から構成されている。 Flat shape which is formed in the tubular member 20 includes a first flat plate portion 21 and the second flat plate portion 22 opposite to the flat line in the shorter diameter direction, first circular formed in an arcuate shape projecting outward respectively in the major axis direction An arcuate curved portion 23 and a second arcuate curved portion 24 are included.

また、インナーフィン２５の両端部は、筒状部材２０内部において両端部第１、第２円弧状湾曲部２３、２４の内周面に沿って密接するように形成されている。具体的には、インナーフィン２５の両端部は、第１、第２円弧状湾曲部２３、２４の同心円状に湾曲して形成されている。また、インナーフィン２５の両端部を除く部位は波状に形成され、インナーフィン２５の山部が第１、第２平板部２１、２２と接するように形成されている。   Further, both end portions of the inner fin 25 are formed so as to be in close contact with the inner peripheral surfaces of the first and second arcuate curved portions 23 and 24 at both ends inside the cylindrical member 20. Specifically, both end portions of the inner fin 25 are formed to be bent concentrically with the first and second arcuate curved portions 23 and 24. The portions of the inner fin 25 excluding both ends are formed in a wave shape, and the crests of the inner fin 25 are formed so as to contact the first and second flat plate portions 21 and 22.

筒状部材２０は、筒状部材２０の長径方向における一端側の第１円弧状湾曲部２３において、第１湾曲部２６と第２湾曲部２７とを重ねた状態でろう付け接合して形成されている。   The tubular member 20 is formed by brazing and joining the first curved portion 26 and the second curved portion 27 at the first arcuate curved portion 23 on one end side in the major axis direction of the tubular member 20. ing.

本実施形態における筒状部材２０とインナーフィン２５は、一枚の板状部材からなり、筒状部材２０の第１湾曲部２６と接合される第２湾曲部２７は、インナーフィン２５の一端部を兼ねている。   The tubular member 20 and the inner fin 25 in the present embodiment are made of a single plate-like member, and the second curved portion 27 joined to the first curved portion 26 of the tubular member 20 is one end portion of the inner fin 25. Doubles as

その結果、本実施形態では、インナーフィン２５の一端部は、第１円弧状湾曲部２３における第１湾曲部２６と密接することとなる。ここで、板状部材として例えばアルミニウム合金を用いることができる。   As a result, in the present embodiment, one end portion of the inner fin 25 is in close contact with the first curved portion 26 in the first arc-shaped curved portion 23. Here, for example, an aluminum alloy can be used as the plate-like member.

インナーフィン２５の筒状部材２０長径方向の長さは、筒状部材２０内の長径方向の長さと同等、若しくは所定寸法以上の長さとなっており、筒状部材２０の第１、第２円弧状湾曲部２３、２４とインナーフィン２５の両端部は、密接してろう付けされる。   The length of the inner fin 25 in the major axis direction of the cylindrical member 20 is equal to the length of the major axis direction in the cylindrical member 20 or a length greater than a predetermined dimension. The first and second circles of the cylindrical member 20 are the same. The arc-shaped curved portions 23 and 24 and both end portions of the inner fin 25 are brazed closely.

ここで、所定寸法とは、インナーフィン２５の端部が、第１円弧状湾曲部２３および第２円弧状湾曲部２４と突っ張る（密接する）際に発生する反力より、インナーフィン２５が弾性変形する範囲の寸法を示している。   Here, the predetermined dimension means that the inner fin 25 is elastic due to a reaction force generated when the end portion of the inner fin 25 is stretched (closely contacted) with the first arc-shaped curved portion 23 and the second arc-shaped curved portion 24. The dimensions of the deformation range are shown.

また、インナーフィン２５の筒状部材２０短径方向の長さは、第１平板部２１と第２平板部２２間の長さと同等となるように形成されている。   The length of the inner fin 25 in the short axis direction of the tubular member 20 is formed to be equal to the length between the first flat plate portion 21 and the second flat plate portion 22.

上述のようにインナーフィン２５の端部が、第１円弧状湾曲部２３および第２円弧状湾曲部２４と突っ張る（密接する）構成としているため、図３に示すようにインナーフィン２５における第１、第２平板部２１、２２と対向する山部２５ａにおいて、突っ張りにより発生する反力Ｐにより、第１円弧状湾曲部２３側の第１平板部２１を外側に向けて押す外力Ｆが発生する。   As described above, since the end of the inner fin 25 is configured to stretch (closely contact) the first arc-shaped curved portion 23 and the second arc-shaped curved portion 24, as shown in FIG. In the mountain portion 25a facing the second flat plate portions 21 and 22, an external force F that pushes the first flat plate portion 21 on the first arcuate curved portion 23 side outward is generated by the reaction force P generated by the tension. .

この外力Ｆは、第１円弧状湾曲部２３における第１湾曲部２６とインナーフィン２５の端部である第２湾曲部２７とを押し開く力として作用する。そのため、筒状部材２０とインナーフィン２５との間のろう付け性が不安定となる可能性がある。   The external force F acts as a force that pushes open the first bending portion 26 in the first arcuate bending portion 23 and the second bending portion 27 that is the end of the inner fin 25. Therefore, the brazing property between the tubular member 20 and the inner fin 25 may become unstable.

そこで、本実施形態では、第１湾曲部２６と第２湾曲部２７との接触部の接触角度θを変化させた場合の筒状部材２０とインナーフィン２５との間のろう付け性についての評価を行なった。ここで、接触角度θは第１円弧状湾曲部２３の円弧中心から第１湾曲部２６とインナーフィン２５の端部（本実施形態では第２湾曲部２７）とが密接する部位の両端部に延びる方向がなす角度を示している。 Therefore, in the present embodiment, evaluation of brazing properties between the tubular member 20 and the inner fin 25 when the contact angle θ of the contact portion between the first bending portion 26 and the second bending portion 27 is changed. Was done. Here, the contact angle θ is at both ends of the portion where the first curved portion 26 and the end of the inner fin 25 (the second curved portion 27 in this embodiment) are in close contact with each other from the arc center of the first arc-shaped curved portion 23. The angle formed by the extending direction is shown.

このろう付け性の評価について図４に基づいて説明する。図４は、外力Ｆの比率と接触角度θとの関係を示している。   This brazing property evaluation will be described with reference to FIG. FIG. 4 shows the relationship between the ratio of the external force F and the contact angle θ.

図４における縦軸は、θ＝１８０°における外力Ｆの平均を１とした場合の各接触角度θにおける外力Ｆの比率を示しており、横軸は接触角度θを示している。なお、本実施形態における接触角度θは、第１円弧状湾曲部２３の円弧中心から第１平板部２１に対して直行する方向をθ＝０°とし、第1湾曲部２６とインナーフィン２５端部（第２湾曲部２７）の接触角度を示している。   The vertical axis in FIG. 4 indicates the ratio of the external force F at each contact angle θ when the average of the external force F at θ = 180 ° is 1, and the horizontal axis indicates the contact angle θ. In the present embodiment, the contact angle θ is θ = 0 ° in the direction orthogonal to the first flat plate portion 21 from the arc center of the first arc-shaped bending portion 23, and the first bending portion 26 and the inner fin 25 end. The contact angle of the portion (second bending portion 27) is shown.

この図４では、接触角度を２０°〜１８０°まで変化させた際の外力Ｆの比率を測定している。なお、測定は８回行なっており、図４における黒丸は、８回の測定の平均値を示しており、上方向の矢印は最大値、下方向の矢印は最小値を示している。   In FIG. 4, the ratio of the external force F when the contact angle is changed from 20 ° to 180 ° is measured. In addition, the measurement was performed 8 times, and the black circles in FIG. 4 indicate the average value of the 8 measurements, the upward arrow indicates the maximum value, and the downward arrow indicates the minimum value.

図４に示すように、外力Ｆの比率は、接触角度θ＝２０°〜６０°では比較的高い値（接触角度θ＝１８０°における外力Ｆの約５倍）を示しており、接触角度θが９０°を超えると外力Ｆの比率の平均値は減少するが、接触角度θ＝９０°では外力Ｆの比率の最大値と最小値でのバラツキが大きい。そのため、筒状部材２０とインナーフィン２５との間のろう付け性が不安定となる可能性がある。   As shown in FIG. 4, the ratio of the external force F shows a relatively high value at the contact angle θ = 20 ° to 60 ° (about 5 times the external force F at the contact angle θ = 180 °). When the angle exceeds 90 °, the average value of the ratio of the external force F decreases. However, when the contact angle θ is 90 °, the variation between the maximum value and the minimum value of the ratio of the external force F is large. Therefore, the brazing property between the tubular member 20 and the inner fin 25 may become unstable.

一方、接触角度θが１１０°以上では、比較的低い値（接触角度θ＝１８０°における外力Ｆと同程度）を示しており、外力Ｆの比率の最大値と最小値でのバラツキも小さく収束している。   On the other hand, when the contact angle θ is 110 ° or more, a relatively low value (similar to the external force F at the contact angle θ = 180 °) is shown, and the variation between the maximum value and the minimum value of the ratio of the external force F is small and converges. is doing.

このため、第１円弧状湾曲部２３における第１湾曲部２６と第２湾曲部２７との接触部における接触角度を１１０°以上になるように第１湾曲部２６を形成することで、外力Ｆを比較的小さい値とすることができる。   For this reason, the external force F is formed by forming the first bending portion 26 so that the contact angle at the contact portion between the first bending portion 26 and the second bending portion 27 in the first arcuate bending portion 23 is 110 ° or more. Can be a relatively small value.

したがって、第１湾曲部２６を、第１湾曲部２６と第２湾曲部２７との接触している部位の接触角度を１１０°以上となるように形成することで、筒状部材２０とインナーフィン２５との間のろう付け性を安定させることができる。   Therefore, the cylindrical member 20 and the inner fin are formed by forming the first bending portion 26 so that the contact angle of the portion where the first bending portion 26 and the second bending portion 27 are in contact is 110 ° or more. The brazing property between 25 can be stabilized.

ところで、本実施形態の第１円弧状湾曲部２３における第１湾曲部２６の先端側部位（板状部材の一端部位）の外側面には、板厚方向の断面が先端方向に向かって徐々に減少するように傾斜部２６ａが形成されている。また、第２湾曲部２７における第１湾曲部２６の傾斜部２６ａに対向する部位は、板厚方向の断面が所定区間において平坦状となるように平坦部２７ａが形成されている。 By the way, on the outer surface of the distal end side portion (one end portion of the plate-like member) of the first curved portion 26 in the first arc-shaped curved portion 23 of the present embodiment, the cross section in the plate thickness direction gradually increases toward the distal direction. An inclined portion 26a is formed so as to decrease. Further, a position facing the inclined portion 26 a of the first bending portion 26 of the second curved portion 27, the thickness direction of the cross section is formed flat portion 27a so as to be flat in the predetermined section.

この第１湾曲部２６の傾斜部２６ａと第２湾曲部２７の平坦部２７ａは、第１湾曲部２６と第２湾曲部２７とを重ね合わせる際に発生する筒状部材２０外周面の段差（隙間）の形成を抑制している。   The inclined portion 26a of the first bending portion 26 and the flat portion 27a of the second bending portion 27 are stepped on the outer peripheral surface of the cylindrical member 20 (the surface of the first bending portion 26 and the second bending portion 27). The formation of gaps is suppressed.

ここで、第２湾曲部２７の平坦部２７ａが形成された所定区間は、筒状部材２０を成形する際の板状部材の寸法バラツキを考慮して形成される区間であって、少なくとも第１湾曲部２６の傾斜部２６ａと接合される区間に形成されている。   Here, the predetermined section in which the flat portion 27a of the second bending section 27 is formed is a section formed in consideration of the dimensional variation of the plate-shaped member when the cylindrical member 20 is molded, and is at least the first section. It is formed in a section joined to the inclined portion 26 a of the bending portion 26.

以上説明したように、筒状部材２０内に形成されたインナーフィン２５は、インナーフィン２５の両端部と対向する第１、第２円弧状湾曲部２３、２４とが互いの反力で突っ張る構造とすることができる。これにより、インナーフィン２５の両端部は、第１、第２円弧状湾曲部２３、２４に沿って密接させることができ、インナーフィン２５の両端部と第１、第２円弧状湾曲部２３、２４のろう付けによる接合のろう付け性を向上させることができる。   As described above, the inner fin 25 formed in the tubular member 20 has a structure in which the first and second arc-shaped curved portions 23 and 24 facing both ends of the inner fin 25 are stretched by the mutual reaction force. It can be. As a result, both end portions of the inner fin 25 can be brought into close contact with the first and second arc-shaped curved portions 23 and 24, and both end portions of the inner fin 25 and the first and second arc-shaped curved portions 23, It is possible to improve the brazing performance of the joint by 24 brazing.

ここで、インナーフィン２５の端部と筒状部材２０端部とが突っ張る構造となるため、第１平板部２１と第２平板部２２とは、互いに近づく方向に力が発生し、平板部２１、２２に対向するインナーフィン２５の山部とを密接させることができる。そのため、平板部２１、２２と平板部２１、２２に対向するインナーフィン２５の接合のろう付け性を向上させることができる。   Here, since the end portion of the inner fin 25 and the end portion of the tubular member 20 are stretched, the first flat plate portion 21 and the second flat plate portion 22 generate a force in a direction approaching each other, and the flat plate portion 21. , 22 can be brought into close contact with the peak portion of the inner fin 25. Therefore, it is possible to improve the brazing property of the joining of the flat plate portions 21 and 22 and the inner fins 25 facing the flat plate portions 21 and 22.

さらに、筒状部材２０とインナーフィン２５を一枚の板状部材で形成することで、インナーフィン２５と筒状部材２０との接合部の接合箇所を減少させることができる。この場合には、第１湾曲部２６を、第１湾曲部２６と第２湾曲部２７（インナーフィン２５の一端部）との接触している部位の接触角度を１１０度以上となるように形成することで、筒状部材２０とインナーフィン２５の山部との間のろう付け性を安定させることができる。   Furthermore, by forming the tubular member 20 and the inner fin 25 with a single plate-like member, the number of joints at the joint between the inner fin 25 and the tubular member 20 can be reduced. In this case, the first bending portion 26 is formed so that the contact angle of the portion where the first bending portion 26 and the second bending portion 27 (one end portion of the inner fin 25) are in contact is 110 degrees or more. By doing so, the brazing property between the cylindrical member 20 and the peak part of the inner fin 25 can be stabilized.

さらにまた、筒状部材２０の第１湾曲部２６の傾斜面２６ａおよび第２湾曲部２７の平坦部２７ａを設けることで、第１湾曲部２６と第２湾曲部２７とを重ね合わせにより発生する段差（隙間）の形成を抑制することができる。   Furthermore, by providing the inclined surface 26a of the first bending portion 26 of the cylindrical member 20 and the flat portion 27a of the second bending portion 27, the first bending portion 26 and the second bending portion 27 are generated by overlapping. Formation of a step (gap) can be suppressed.

これは、筒状部材２０の長手方向端部をタンク５のコアプレート５ａの挿入部に挿入して接合する際に、第１湾曲部２６の先端位置が塑性変形して伸ばされ、筒状部材２０の長手方向端部とコアプレート５ａの挿入部との隙間を微小化することができるためである。その結果、ラジエータ１（熱交換器）の接合部のろう付け性を向上させることができる。
This is when bonding by inserting the longitudinal end of the tubular member 20 into the insertion portion of the core plate 5a of the tank 5, the tip position of the first bending portion 26 is extended by plastic deformation, the tubular member This is because the gap between the longitudinal end portion of 20 and the insertion portion of the core plate 5a can be miniaturized. As a result, it is possible to improve the brazing performance of the joint portion of the radiator 1 (heat exchanger).

したがって、本実施形態におけるインナーフィンチューブ２は、筒状部材２０内部に設けられたインナーフィン２５の配設性を確保しつつ、インナーフィンチューブ２の接合部におけるろう付け性を向上させることができる。   Therefore, the inner fin tube 2 in the present embodiment can improve the brazing performance at the joint portion of the inner fin tube 2 while ensuring the disposition of the inner fin 25 provided inside the cylindrical member 20. .

（第２実施形態）
次に、本発明の第２実施形態について図５に基づいて説明する。本第２実施形態では、上記第１実施形態と異なる部分についてのみ説明する。図５は、本実施形態に係るインナーフィンチューブ２の冷却水流通方向と直交する断面の断面図を示している。 (Second Embodiment)
Next, a second embodiment of the present invention will be described with reference to FIG. In the second embodiment, only parts different from the first embodiment will be described. FIG. 5 shows a cross-sectional view of a cross section orthogonal to the coolant flow direction of the inner fin tube 2 according to the present embodiment.

上記第１実施形態では、インナーフィンチューブ２は、１枚の板状部材で形成されている。本実施形態では、インナーフィンチューブ２における筒状部材２０とインナーフィン２５は、それぞれ１枚の板状部材で形成され、筒状部材２０内部にインナーフィン２５を配置することでインナーフィンチューブ２を構成している。   In the first embodiment, the inner fin tube 2 is formed of a single plate-like member. In the present embodiment, the tubular member 20 and the inner fin 25 in the inner fin tube 2 are each formed of a single plate-like member, and the inner fin tube 2 is disposed by arranging the inner fin 25 inside the tubular member 20. It is composed.

筒状部材２０とインナーフィン２５をそれぞれ１枚の板状部材で形成する場合、インナーフィン２５の板状部材を筒状部材２０の板状部材よりも板厚を薄くすることができる。これにより、インナーフィンチューブ２の重量や内部流体抵抗を抑制しつつ、内部表面積を増大することができる。   When the tubular member 20 and the inner fin 25 are each formed of a single plate member, the plate member of the inner fin 25 can be made thinner than the plate member of the tubular member 20. Thereby, the internal surface area can be increased while suppressing the weight of the inner fin tube 2 and the internal fluid resistance.

図５に示すように、本実施形態のインナーフィンチューブ２は、インナーフィン２５の端部が、第１湾曲部２６、第２湾曲部２７と密接する構成となっている。   As shown in FIG. 5, the inner fin tube 2 of the present embodiment has a configuration in which the end of the inner fin 25 is in close contact with the first bending portion 26 and the second bending portion 27.

そのため、インナーフィン２５の一端部は、第１湾曲部２６、第２湾曲部２７を接合する際に、第１湾曲部２６、第２湾曲部２７に挟持される。   Therefore, one end portion of the inner fin 25 is sandwiched between the first bending portion 26 and the second bending portion 27 when the first bending portion 26 and the second bending portion 27 are joined.

これにより、インナーフィン２５端部と対向する第１円弧状湾曲部２３（第１湾曲部２６）、第２円弧状湾曲部２４とが互いの反力で突っ張る構造とすることができる。さらに、インナーフィン２５の一端部が第１湾曲部２６、第２湾曲部２７に挟持されるため、インナーフィン２５の一端部と筒状部材２０内周面の接合におけるろう付け性を向上させることができる。   Thereby, it can be set as the structure where the 1st circular arc-shaped curved part 23 (1st curved part 26) and the 2nd circular arc-shaped curved part 24 which oppose the edge part of the inner fin 25 are stretched with a mutual reaction force. Furthermore, since the one end part of the inner fin 25 is clamped by the 1st bending part 26 and the 2nd bending part 27, the brazing property in joining of the one end part of the inner fin 25 and the cylindrical member 20 inner peripheral surface is improved. Can do.

（第３実施形態）
次に、本発明の第３実施形態について図６に基づいて説明する。本第３実施形態では、上記第２実施形態と異なる部分についてのみ説明する。図６は、本実施形態に係るインナーフィンチューブ２の冷却水流通方向と直交する断面の断面図を示している。 (Third embodiment)
Next, a third embodiment of the present invention will be described with reference to FIG. In the third embodiment, only parts different from the second embodiment will be described. FIG. 6 shows a cross-sectional view of a cross section orthogonal to the coolant flow direction of the inner fin tube 2 according to the present embodiment.

上記第２実施形態のインナーフィンチューブ２では、インナーフィン２５の端部が、第１湾曲部２６、第２湾曲部２７と密接する構成となっている。   In the inner fin tube 2 of the second embodiment, the end portion of the inner fin 25 is in close contact with the first bending portion 26 and the second bending portion 27.

本実施形態のインナーフィンチューブ２では、筒状部材２０の第１円弧状湾曲部２３を形成する第１湾曲部２６、第２湾曲部２７が接合された後にインナーフィン２５を挿入するため、図４に示すようにインナーフィン２５の端部は、第１湾曲部２６と第２湾曲部２７とから構成される第１円弧状湾曲部２３の内周面と密接する構成となっている。   In the inner fin tube 2 of the present embodiment, the inner fin 25 is inserted after the first curved portion 26 and the second curved portion 27 forming the first arcuate curved portion 23 of the cylindrical member 20 are joined. As shown in FIG. 4, the end portion of the inner fin 25 is in close contact with the inner peripheral surface of the first arcuate curved portion 23 composed of the first curved portion 26 and the second curved portion 27.

これによっても、インナーフィン２５端部と対向する第１円弧状湾曲部２３、第２円弧状湾曲部２４とが互いの反力で突っ張る構造とすることができる。従って、インナーフィン２５の一端部と筒状部材２０内周面の接合部におけるろう付け性を向上させることができる。   Also by this, it can be set as the structure where the 1st circular arc-shaped curved part 23 and the 2nd circular arc-shaped curved part 24 which oppose the inner fin 25 edge part are stretched | stretched by mutual reaction force. Accordingly, it is possible to improve the brazing performance at the joint portion between the one end portion of the inner fin 25 and the inner peripheral surface of the tubular member 20.

（第４実施形態）
次に、本発明の第４実施形態について図７に基づいて説明する。本第４実施形態では、上記第３実施形態と異なる部分についてのみ説明する。図７は、本実施形態に係るインナーフィンチューブ２の冷却水流通方向と直交する断面の断面図を示している。 (Fourth embodiment)
Next, a fourth embodiment of the present invention will be described with reference to FIG. In the fourth embodiment, only parts different from the third embodiment will be described. FIG. 7 shows a cross-sectional view of a cross section orthogonal to the coolant flow direction of the inner fin tube 2 according to the present embodiment.

上記第３実施形態のインナーフィンチューブ２では、筒状部材２０における第１円弧状湾曲部２３の内周および外周面は略円弧状になるように、第１湾曲部２６と第２湾曲部２７とが重ね合うように形成されている。   In the inner fin tube 2 of the third embodiment, the first curved portion 26 and the second curved portion 27 are formed so that the inner circumference and the outer circumferential surface of the first arc-shaped curved portion 23 in the cylindrical member 20 are substantially arc-shaped. And are formed to overlap each other.

本実施形態では、図７に示すように筒状部材２０の第１湾曲部２６、第２湾曲部２７の先端部は、それぞれ筒状部材２０長径方向外部に向かって折り曲げた曲げ部２８を有している。   In the present embodiment, as shown in FIG. 7, the distal end portions of the first bending portion 26 and the second bending portion 27 of the tubular member 20 have bent portions 28 that are bent outward in the longitudinal direction of the tubular member 20. is doing.

そして第１湾曲部２６、第２湾曲部２７のそれぞれの曲げ部２８同士を接合することで、第１円弧状湾曲部２３の内周面が円弧状となるように形成している。ここで、第１円弧状湾曲部２３内周を半分に分けた際の第１平板部２１側が第１湾曲部２６を構成し、第２平板部２２側が第２湾曲部２７を構成している。   Then, by joining the bent portions 28 of the first bending portion 26 and the second bending portion 27, the inner peripheral surface of the first arc-shaped bending portion 23 is formed in an arc shape. Here, when the inner circumference of the first arcuate curved portion 23 is divided in half, the first flat plate portion 21 side constitutes the first curved portion 26, and the second flat plate portion 22 side constitutes the second curved portion 27. .

ただし、筒状部材２０の第１円弧状湾曲部２３の外側に曲げ部２８を形成するため、タンク５のコアプレート５ａに本実施形態の筒状部材２０の外周形状に合わせた接合部を形成する必要がある。   However, in order to form the bent portion 28 outside the first arcuate curved portion 23 of the tubular member 20, a joint portion that matches the outer peripheral shape of the tubular member 20 of the present embodiment is formed on the core plate 5a of the tank 5. There is a need to.

これにより、インナーフィン２５の端部と対向する第１円弧状湾曲部２３、第２円弧状湾曲部２４の内周面とが互いの反力で突っ張る構造とすることができる。従って、インナーフィン２５の一端部と筒状部材２０内周面の接合部のろう付け性を向上させることができる。   Thereby, it can be set as the structure where the inner peripheral surface of the 1st circular arc-shaped curved part 23 and the 2nd circular arc-shaped curved part 24 which opposes the edge part of the inner fin 25 stretches with mutual reaction force. Therefore, it is possible to improve the brazability of the joint portion between the one end portion of the inner fin 25 and the inner peripheral surface of the tubular member 20.

（他の実施形態）
（１）上記各実施形態では、本発明に係る熱交換器をラジエータに適用した例について説明したが、これに限らず、ヒータコアユニット、エバポレータ等の各種の熱交換器に適用してもよい。この場合、熱交換媒体としては、エンジン冷却水以外のものを用いてもよい。 (Other embodiments)
(1) In each of the above embodiments, an example in which the heat exchanger according to the present invention is applied to a radiator has been described. However, the present invention is not limited thereto, and may be applied to various heat exchangers such as a heater core unit and an evaporator. In this case, a heat exchange medium other than engine cooling water may be used.

（２）また、上記第２〜第４実施形態では、１枚の板状部材で形成される筒状部材２０は、第１円弧状湾曲部２３で接合しているが、これに限られない。例えば、筒状部材２０を２枚の板状部材で構成し、第１、第２円弧状湾曲部２３、２４において２枚の板状部材を接合してもよい。   (2) Moreover, in the said 2nd-4th embodiment, although the cylindrical member 20 formed with one plate-shaped member is joined by the 1st circular arc-shaped curved part 23, it is not restricted to this. . For example, the cylindrical member 20 may be constituted by two plate-like members, and the two plate-like members may be joined at the first and second arcuate curved portions 23 and 24.

（３）また、上記各実施形態では、筒状部材２０の長径方向に第１、第２円弧状湾曲部２３、２４が円弧状に形成されているが、円弧状に限られず、例えば曲率半径の異なる円を組み合わせた形状等であってもよい。   (3) In each of the above embodiments, the first and second arc-shaped curved portions 23 and 24 are formed in an arc shape in the major axis direction of the cylindrical member 20, but the shape is not limited to the arc shape, for example, a radius of curvature. The shape etc. which combined the different circle | round | yen may be sufficient.

（４）また、上記第１実施形態では、第１湾曲部２６の先端部位（板状部材の一端部）が、断面が先端方向に向かって徐々に減少するように板状部材に傾斜部２６ａが形成されているが、これに限られない。   (4) Moreover, in the said 1st Embodiment, it is an inclined part 26a to a plate-shaped member so that the front-end | tip part (one end part of a plate-shaped member) of the 1st bending part 26 may reduce a cross section gradually toward a front-end | tip direction. However, it is not limited to this.

例えば、図８に示すように、傾斜部２６ａは両テーパ状（板状部材の両面に傾斜面が設けられた状態）に形成されていてもよい。この場合、第１湾曲部２６の先端部位の板厚方向の断面は、先端に向かってテーパ状に細くなった台形形状（図８（ａ）に示す形状）であってもよいし、先端に向かってテーパ状に細くなった三角形状（図８（ｂ）に示す形状）であってもよい。さらに、傾斜部２６ａは、片面側若しくは両面側が先端に向かって板厚方向の断面積が減少するように円弧状に形成されていてもよい（図８（ｃ）〜（ｅ）に示す形状）。   For example, as shown in FIG. 8, the inclined portion 26a may be formed in both tapered shapes (a state where inclined surfaces are provided on both surfaces of the plate-like member). In this case, the cross section in the plate thickness direction of the distal end portion of the first bending portion 26 may have a trapezoidal shape (the shape shown in FIG. 8A) that tapers toward the distal end, It may be a triangular shape (shape shown in FIG. 8B) that is tapered toward the bottom. Furthermore, the inclined portion 26a may be formed in an arc shape so that the cross-sectional area in the plate thickness direction decreases toward the tip on one side or both sides (the shapes shown in FIGS. 8C to 8E). .

本発明の第１実施形態におけるラジエータを示す正面図である。It is a front view which shows the radiator in 1st Embodiment of this invention. 本発明の第１実施形態のインナーフィンチューブにおける冷却水流通方向と直交する断面の断面図である。It is sectional drawing of the cross section orthogonal to the cooling water flow direction in the inner fin tube of 1st Embodiment of this invention. 本発明の第１実施形態のインナーフィンチューブにおける冷却水流通方向と直交する断面の部分断面図である。It is a fragmentary sectional view of the cross section orthogonal to the cooling water distribution direction in the inner fin tube of 1st Embodiment of this invention. 第１実施形態における外力Ｆの比率と接触角度との関係を示す実験データのグラフである。It is a graph of the experimental data which shows the relationship between the ratio of the external force F in 1st Embodiment, and a contact angle. 本発明の第２実施形態のインナーフィンチューブにおける冷却水流通方向と直交する断面の断面図である。It is sectional drawing of the cross section orthogonal to the cooling water flow direction in the inner fin tube of 2nd Embodiment of this invention. 本発明の第３実施形態のインナーフィンチューブにおける冷却水流通方向と直交する断面の断面図である。It is sectional drawing of the cross section orthogonal to the cooling water flow direction in the inner fin tube of 3rd Embodiment of this invention. 本発明の第４実施形態のインナーフィンチューブにおける冷却水流通方向と直交する断面の断面図である。It is sectional drawing of the cross section orthogonal to the cooling water flow direction in the inner fin tube of 4th Embodiment of this invention. 筒状部材の第１弧状湾曲部付近を示す拡大横断面図である。It is an expanded cross-sectional view which shows the 1st arc-shaped curved part vicinity of a cylindrical member.

符号の説明Explanation of symbols

１…ラジエータ（熱交換器）、２…インナーフィンチューブ（熱交換器用チューブ）、２０…筒状部材、２１…第１平板部、２２…第２平板部、２３…第１円弧状湾曲部、２４…第２円弧状湾曲部、２５…インナーフィン、２６…第１湾曲部、２６ａ…傾斜部、２７…第２湾曲部、２７ａ…平坦部。   DESCRIPTION OF SYMBOLS 1 ... Radiator (heat exchanger), 2 ... Inner fin tube (heat exchanger tube), 20 ... Cylindrical member, 21 ... 1st flat plate part, 22 ... 2nd flat plate part, 23 ... 1st circular arc-shaped curved part, 24 ... second arcuate curved portion, 25 ... inner fin, 26 ... first curved portion, 26a ... inclined portion, 27 ... second curved portion, 27a ... flat portion.

Claims (5)

熱交換媒体が流通するとともに、熱交換媒体の流通方向と直交する流路断面が扁平形状に形成された板状部材からなる筒状部材（２０）と、
前記筒状部材（２０）の内部に設けられ、熱交換媒体との伝熱面積を増大させるインナーフィン（２５）とがろう付けにより接合された熱交換器用チューブにおいて、
前記筒状部材（２０）は、前記筒状部材（２０）の前記流路断面の短径方向において平行に対向する一対の平板部（２１、２２）と、前記筒状部材（２０）の前記流路断面の長径方向において前記筒状部材（２０）の両端部の内面側が弧状に形成された一対の弧状湾曲部（２３、２４）とを有しており、
前記インナーフィン（２５）は、前記弧状湾曲部（２３、２４）の内面に対向する端部が、前記弧状湾曲部（２３、２４）の内周面に沿って密接するように形成されており、
前記筒状部材（２０）は、前記一対の弧状湾曲部（２３、２４）のうち少なくとも一方の前記弧状湾曲部（２３、２４）に前記板状部材相互の接合部を有し、前記接合部において前記板状部材の一端部であって弧状に形成された第１湾曲部（２６）と、前記第１湾曲部（２６）の内周面に重ね合うように弧状に形成された第２湾曲部（２７）とが接合されており、
前記第２湾曲部（２７）における少なくとも前記第１湾曲部（２６）の先端部位（２６ａ）の内周面に対向する部位の外周面に、この外周面の周方向に延びる平坦部（２７ａ）が形成され、
前記平坦部（２７ａ）は湾曲面の一部を平坦にした段差のない形状で前記第２湾曲部（２７）の外周面に接続され、
前記第１湾曲部（２６）の前記先端部位（２６ａ）が前記平坦部（２７ａ）上に重ね合うようになっていることを特徴とする熱交換器用チューブ。 A cylindrical member (20) composed of a plate-like member in which a heat exchange medium flows and a cross section of a flow path perpendicular to the flow direction of the heat exchange medium is formed in a flat shape,
In the tube for a heat exchanger provided inside the tubular member (20) and joined by brazing with an inner fin (25) that increases the heat transfer area with the heat exchange medium,
It said tubular member (20) includes a pair of plate portions (21, 22) facing the flat line in the shorter diameter direction of the flow path cross-section of the tubular member (20), said tubular member (20) A pair of arcuate curved portions (23, 24) in which inner surface sides of both ends of the tubular member (20) are formed in an arc shape in the major axis direction of the flow path cross section,
Said inner fin (25) has an end which faces the inner surface of the arcuate curved portions (23, 24) is formed so as to closely along the inner peripheral surface of the arcuate curved portions (23, 24) ,
The cylindrical member (20) has a joint part between the plate-like members in at least one arcuate curved part (23, 24) of the pair of arcuate curved parts (23, 24). And a second curved portion formed in an arc shape so as to overlap the inner peripheral surface of the first curved portion (26). (27) is joined,
A flat portion (27a) extending in the circumferential direction of the outer peripheral surface on at least the outer peripheral surface of the second curved portion (27) facing the inner peripheral surface of the distal end portion (26a) of the first curved portion (26). Formed,
The flat portion (27a) is connected to the outer peripheral surface of the second curved portion (27) in a shape having no step where a part of the curved surface is flattened,
The tube for a heat exchanger , wherein the distal end portion (26a) of the first bending portion (26) is overlapped on the flat portion (27a) . 前記筒状部材（２０）と前記インナーフィン（２５）は、１枚の板状部材により一体に形成されていることを特徴とする請求項１に記載の熱交換器用チューブ。 Wherein said tubular member (20) inner fin (25), the heat exchanger tube according to claim 1, characterized in Tei Rukoto are integrally formed by one plate-like member. 前記弧状湾曲部（２３、２４）と、前記インナーフィン（２５）における前記弧状湾曲部（２３、２４）の内周面とが密接している部位の接触角度は、１１０°以上であることを特徴とする請求項２に記載の熱交換器用チューブ。   The contact angle of the portion where the arc-shaped curved portion (23, 24) and the inner peripheral surface of the arc-shaped curved portion (23, 24) in the inner fin (25) are in close contact is 110 ° or more. The heat exchanger tube according to claim 2, wherein: 前記筒状部材（２０）と前記インナーフィン（２５）は、それぞれ異なる板状部材で構成されていることを特徴とする請求項１に記載の熱交換器用チューブ。   The tube for a heat exchanger according to claim 1, wherein the cylindrical member (20) and the inner fin (25) are respectively configured by different plate-like members. 前記第１湾曲部（２６）の前記先端部位（２６ａ）は、先端に向かって前記板状部材の板厚さ方向の断面積が徐々に減少するように形成されていることを特徴とする請求項１ないし４のいずれか１つに記載の熱交換器用チューブ。 The distal end portion of the first bending portion before Symbol (26) (26a) is characterized in that the cross-sectional area of the plate thickness direction of the plate-like member toward the distal end is formed so as to gradually decrease The heat exchanger tube according to any one of claims 1 to 4.
JP2007181965A 2007-07-11 2007-07-11 Tube for heat exchanger Expired - Fee Related JP4952414B2 (en)

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US12/515,392 US8925625B2 (en) 2007-07-11 2008-07-10 Heat exchanger
BRPI0806229A BRPI0806229B8 (en) 2007-07-11 2008-07-10 heat exchanger
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JP5861549B2 (en) 2012-04-04 2016-02-16 株式会社デンソー Tube and heat exchanger provided with the tube
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